bergevin



Aug. 20, 1957 c. R. BERGEVIN SPRING comme MACHINE 4 Sheets-Sheet 2Original Filed Dec.

INVENTOR.

CHARLES ze. ffV// 7" QA/EY AU8- 20, 1957 c. R. BERGEVIN Re. 24,345

SPRING COILING MACHINE original Enea nec. 16.*1954 4 Sheets-Sheei'; 3

I krO/Q/VY ug- 20, 1957r c. R. BERGEVIN Re. 24,345

1 SPRING coILING MACHINE "original Filed nec. 1e. 1954 Y 4 sneetssheet 4A* ff);

United States Patent fice l Re. Reissued Aug. 20, 1957 SPRING COILINGMACHINE Charles R. Bergevin, Torrington, Conn., assignor to TheTorrington Manufacturing Company, Torrington, Conn., a corporation ofConnecticut Original No. 2,765,022, dated October 2, 1956, Serial No.475,686, December 16, 1954. Application for reissue March 14, 1957,Serial No. 646,186

23 Claims. (Cl. 153-65) Matter enclosed in heavy brackets appears in theoriginal patent but forms no part of this reissue specification; matterprinted in italics indicates the additions made by reissue.

This invention relates to a cyclically operable spring making machinewherein the springs are formed by the ceiling of a longitudinally movingwire as the result of engagement thereof with a relatively fixed ceilingpoint, and the invention relates more particularly to a machine of thetype wherein' the longitudinal movement of the wire is effected by afeed mechanism including wire engaging means and including a recprocableor oscillable means 'having one reciprocation or oscillation during eachmachine cycle. 'A machine of the said type is shown in the Bergevin andNigro Patent No. 2,119,002 for Spring Coiling Machine, dated May 3,1938.

ln a machine o f the type referred to, as exemplified in the `saidpatent, the wire engaging means of the feed mechanism is operable onlyduring movement of the reciprocating means in one direction, the saidfeed mechanism therefore being idle during a large portion of each cycleof the machine. The general object of the present invention is toprovide a spring coiling machine wherein the wire engaging means of the.feed mechanism is operable `during movement of said reciprocating meansin both directions, the wire engaging means therefore being operableduring a `much large portion of each cycle Of the machine with acorresponding increase in the productive capacity of the machine.

Another general object of the invention is to provide a machine havingthe characteristics above set forth and having during each cycle atleast one 'interval of time intervening between successive feedingmovements and 'having a cutoff mechanism which is operated during eachcycjle'and during said intervening interval, at least one spring beingformed and cut off during each cycle.

' Another general object of the invention is to provide a machine havingsaid characteristics and having two separate Wire feeding movementsduring each cycle with intervals o f time between successive movementsand having a cutoli mechanism which is operated twice `during eachcycle, two springs being formed and cut o t during each cycle.

Still another general object of the invention is Ato provide a machinehaving the characteristics set forth in the last preceding paragraphandalso .having means operated twice during each cycle for varying thediameter or the pitch or both the diameter and the pitch of two springsvformed during each cycle.

Still another object of the invention is to provide a machine having-some or allof the characteristics above and combinations ofsuchfeatures which facilitate the attainment of said more generalobjects of the invention.

AThe accompanying drawings show in detail one embodiment of theinvention and show schematically several alternative embodiment of theinvention. It will be understood that the drawings are not to beconstrued as defining or limiting the scope vof the invention, theclaims forming a part of this specification being relied upon' for thatpurpose.

Fig. 1 is a combined front elevational and sectional view of a springcoiling machine embodying the inverttion, the sectional portion of theviewbeing taken along the line 1-1 of Fig. 2.

Fig. 2 is a left side View of the machine with cover plates omitted, aportion of the machine at the left be tween the intermediate and rearframe members being in' section along the line 2--2 of Fig. l.

Fig. 3 is a fragmentary sectional view of the machine taken along theline 3 3 of Fig. i1.

Fig. 4 is a schematic view showing the action of one of the gearsegments that drive the feed rolls.

Fig. 5 is a View similar to Fig. 4 but showing lthe action of the otherof the gear segments.

Fig. 6 is a diagram showing the timing incident to one gear segment.

Fig. 6a is a diagram similar to Fig. 6 but showing the timing incidentto the other gear segment.

Fig. 7 `is a diagram similar to Fig. 6 but showing the combined timingincident ,to both gear segments.

Fig. 8 is a diagram similar to Fig. 7 but showing the timing incident toan alternative .manner of machine operation.

Fig. 9 is a schematic view somewhat similar to Fig. v4 but showing analternative embodiment of the invention.

Fig. 10 is a view similar to Fig. 9 but showing some of the parts indiiferent positions.

Fig. 1l is a schematic view similar to Fig. 9, but showing anotheralternative embodiment of the invention.

Fig. l2 is a schematic View similar to Fig. 9 but show.- ing st illanother alternative embodiment of the invention.

Fig. 13 is a diagram similar to Fig. l7 .but showing the timing incidentto the mechanism shown in Fig. 12.

Figs. 1 to 3 of the drawings show a machine generally similar to thatshown in the said Patent 2,119,002 :but having different and additionalmechanism `towhich the present vinvention more particularly relates.Reference is made to the said patent for any details o f construction ormanner of operation not herein fully `disclosed.

The ymachine comprises spaced upright frame members 10, 1,2 and 14mounted on a suitable base 16, with the various wire feeding and ceilingdevices ymounted on the front frame member 10 and with the severalmechanisms foroperating ysaid devices mounted between themembers 10 and12 or between the members 1 2 -and 14. The machine may have cover plateso n the sides thereof secured to said frame members, but such plates areomit,- ted Lfrom ythe drawings for clarity of illustration.

The line of wire feed is indicated at 18 in Fig. 1, the wire being fedthrough a preliminary guide 20 and between pairs of cooperatingrotatable feed rolls 22, 24 and 2.6, 2S. The feed vrolls lwhen rotated.serve to lproject the wire vtoward the left so as to .be engaged'bywire ceiling tools or devices as .hereinafterdescribed in detail. Wireguides 30 are provided Abetween the feed rolls 2 2, 24 and the feedrolls 2 6, 28 and additional-wire guides 32 are provided between thefeed rolls 26, t28 and. the coiling devices.

The feed rolls 22, 24 are carried by shafts*3 4,.=3,6 and the feed rolls26, 28 are carried by shafts 3840,.all of the said Shafts -being mountedin bearings in the frame members 41!) and 12. The shafts 3 8, 4 0 areconnected by meshing 4gears 42, 44 and the shafts 34, '36 areconnectedby similar meshing gears which are not shown.

The shafts 34 and 38 for the upper feed rolls 22 and 26 are capable ofslight vertical movement, being mounted in vertically movable bearingblocks 46 and 48. A bowed spring 50 is provided which rests at its endsupon the bearing blocks 46 and 48 and which is engaged by a hand wheel52 engaging a threaded member 54. By turning the hand wheel 52, thespring 50 may be relatively attened to apply downward pressure to thebearing blocks 46 and 48 and to thus apply downward pressure` to thefeed` rolls 22 and 26 so that they grip the wire. l

The lower feed roll shafts 36 and 40 are extended toward the rear of themachine and have additional bear` ings in the rear frame member 14. Theshaft 40 is provided with a gear 56 and the shaft 36 has 'a similar gear57 which is shown only in Figs. 4 and 5. Both of the last said gearsmesh with a gear S8 on a feed shaft 60 mounted in suitable bearings inthe frame members 12 and 14. The feed shaft 60 is rotated by themechanism and in the manner to be described and, when rotated, itrotates the shafts 36 and 40 which in turn rotate the several feed rollsfor feeding the wire toward the left as previously stated.

A mainvdrive shaft 62 is provided, this being mounted in suitablebearings in the frame members 12 and 14. The drive shaft 62 iscontinually driven, as for instance by a motor 64, the motor beingconnected with the shaft by belts 65 engaging a belt pulley 66 securedto said shaft.

For rotating the feed shaft 60 in the feeding direction thereof, thereis provided a reciprocable means having gear teeth spaced in thedirection of reciprocation and there is also provided means operable bythe drive shaft 62 for causing one complete reciprocation of thereciprocable means during each cycle of the machine. The reciprocable.means may be widely varied as will be hereinafter fully apparent but,as shown in Figs. l to 3, the feed means comprises two separateoppositely reciprocable members 68 and 70 which are preferably gearsegments separately movable about a common horizontal pivotal axis. Thesaid members or gear segments are hereinafter referred to as the rst andsecond members or gear segments. As shown, said gear segments aremounted for pivotal movement on a horizontal pivot rod 72 extendingbetween the frame members 12 and 14.

Two gears 74 and 76 are provided which mesh with the teeth ofreciprocable means and each of which is rotatable thereby in onedirection during the first portion of each cycle and is rotatablethereby in an opposite direction during the second portion of eachcycle. As shown,

the gears 74 yand 76 are mounted directly on the feed I shaft 60. butsuch mounting is not essential as will be hereinafter fully apparent.When there are two separate gear segments such as 68 and 70 as shown,said gears 74 and 76 mesh respectively with the teeth of said segments,the gears being hereinafter referred to as the first and second gears.

Unidirectional clutches 78 and 80 are operatively interposedrespectively between the gears 74 and 76 and the feed shaft 60. Whensai-d gears are mounted directly on the feed shaft as shown, theclutches are also mounted directly on the feed shaft, but when the gearsare otherwise mounted the clutches may be also otherwise mounted. Theunidirectional clutches rnay be of any usual or preferred type and eachof them has its driving element connected with the corresponding gear 74or 76 and has its driven element connected with the feed shaft 60. Theclutches are so constructed that each of them serves to drive the feedshaft only in the feeding direction, and in the machine as shown thefeeding direction is the clockwise direction.

For oscillating the gear segments 68 and 70 there are provided twooppositely disposed crankpins 82 and 84 which are rotatable about acommon horizontal axis parallel wtih the axis of oscillation, thecrankpins being entered in radial slots 86 and 88 formed respectively inthe 4 gear segments 68 and 70. Ball bearings 90 and 92 respectivelysurround the crankpins 82 and 84, the outer races of the ball bearingsengaging the side walls of the radial slots 86 land 88 in the segments68 and 70. A crankpin and its bearing are herein sometimes referred tocollectively as a crankpin.

The crankpins 82 and 84 carried respectively by gears 94 and 96 whichare rotatably mounted on studs 98 and projecting respectively from theframe members 12 and 14. The gears 94 and 96 mesh respectively withgears 102 and 104 secured to the drive shaft 62 and the gears 94 and 96are therefore rotated in the same direction and at the same speed. Thecrankpins 82 and 84 are mounted indirectly on the gears 94 and 96 bymeans of blocks 106 and 108 adjustable by means of screws and 112 forchanging the distances of the crankpins 82 and 84 from the axis ofrotation. i

By means of the screws 110 and 112 the pins 82 and 84 may be adjusted tochange the amplitude of oscillation of the gear segments 68 and 70.Ordinarily the two seg'- ments will have the same amplitude `ofoscillation, but they may have different amplitudes. For some purposes,one of the pins may be moved to dead center so that the correspondingsegment will have zero amplitude, that is, it will be stationary. l

The gears 94 and 96 are continually rotated and as they rotate. the gearsegments 68 and 70 are caused to make one complete reciprocation duringeach complete rotation of the gears, that is, during each cycle of themachine; Inasmuch as the crankpins 82 and 84 are oppositely disposed,the gear -segments 68 and 70 reciprocate oppositely with each gearsegment moving in a direction opposite to that of the other.

Referring more particularly to Figs. 4 to 7, each cycle of the machinemay be regarded as starting with the movement of the gear segment 68toward the left, the gear segment 70 moving toward the right during thefirst portion of the cycle. During said first portion of the cycle thegear 74 is moved in the clockwise direction and the clutch 78 operatesto drive the feed shaft in the clockwise direction, that is, in thefeeding direction. During said first portion of the cycle the gear 76 isrotated in the counterclockwise direction, the clutch 80 beingineffective to drive the feed shaft. During the second portion of thecycle the gear segment 68 is moved toward the right and the gear 74 ismoved in the counterclockwise direction, the clutch 78 being ineffectiveto drive the feed shaft. During said second portion -of the cycle thegear segment 70 moves toward the left and the gear 76 is moved in theclockwise direction and the clutch 80 operates to drive the said shaftin the clockwise direction, that is, in the feeding direction. From theforegoing it will be apparent that through the alternating action of thetwo gear segments and the corresponding gears and clutches, the feedshaft 60 is driven in the feeding direction during both portions of eachcycle.

The drive shaft 62 may be driven in either direction but when thesegments, gears and clutches are constructed and arranged as shown, thedrive shaft is advantageously rotated in the counterclockwise direction,the gears 94` and 96 and the crankpins 82 and 84 resultantly rotating inthe clockwise direction. Due to the relationship of the crankpins to thepivotal axis, each pin moves its gear segment faster in one directionthan in the opposite direction, that is, each gear segment is moved inone direction in a little less than a half-cycle and is moved in theopposite direction in a little more than a half-cycle. Referring toFigs. 4 and 6, `each cycle begins with the pin 82 at the extreme rightposition 82a which is somewhat beyond or below a line x--x extendingthrough the axes of the studs 98 and '100 and perpendicular 'to a planethrough the last said axes and the axis of the pivot rod 72. The pinmoves clockwise from the position 82a to the opposite extreme leftposition 82b and correspondingly moves the segment 68 toward the left asindicated by the arrow in a period that is a little less than ahalf-cycle as represented by A. The lgear 74 is correspondingly rotatedyand the action of the clutch 78 is such that the feed rolls rotate inthe feeding direction during said period. The pin 82 then movesclockwise from the left position 82b to the right position 82a andcorrespondingly moves the segment 68 toward the right in a period thatis a little more than a half-cycle as represented by B. The gear iscorrespondingly rotated but there is no feeding by the cl-utch 78 duringthe last said period.

Referring to Figs. and 6a, it will be seen that the pin 84 movesclockwise from the extreme left position 84D tothe extreme rightposition 84et and correspondingly moves the segment 70 toward the lrightin a period that isl a little more than a half-cycle, said period beingof the same duration as the period B. The gear 76' is correspondinglyrotated but there is no feeding by the clutch 80 during the last saidperiod. Position 84aL of the pin 84 as shown in Fig. 5 is in alignmentwith position 82a of the pin 82 as shown in Fig. 4, but the actual pinsare 180 apart and are never in alignment. The described movement of thesegment 70 toward the right from the Fig. 5 position is substantiallysimultaneous with the described movement of the segment 68 toward theleft from the Fige 4 position. The pin 84 then moves clockwise from theright position 84a to the left position 84b and correspondingly movesthe segment 70 toward the left as indicated by the arrow in a periodthat is a little less than a half-cycle, said period being of the sameduration as the period A. The gear 78 is correspondingly rotated and theaction of the clutch 80 is such that the feed rolls rotate in thefeeding direction through the last said period. The two periods ofrotation of the feed rolls resulting from the action of the segments .63and 70 are within the same cycle but they are in opposite phase. It willbe observed that, at the beginning of the cycle as shown in Fig. 4, thepin 84 is at the position 84c which is diametrically opposite theposition 82a of the pin 82. It is therefore evident that, at thebeginning of the cycle, the pin 84 has moved beyond its extreme position84b at the left and has already started to move the segment 70 towardthe right.

Fig. 7 shows the feeding period A for the segment 68 which is the sameas shown in Fig. 6, and Fig. 7 also shows the feeding period for thesegment 70 which is identified as C and which is of the same duration asthe period A but in opposite phase. Inasmuch as each of the periodsl Aand C is less than a half-cycle, there are intervals D and E betweenthem as indicated in Fig. 7. During each feeding movement the feedingspeed is increased from zero to a maximum and is thenldecreased f romthe maximum to zero. The feed rolls are idle or stationary during theintervals D and E. The described construction and arrangement of thecrankpins and the gear segments and the gears and the clutchesconstitute means for providing said intervals D and E.

The extent of wire feeding during the respective portions of each cyclecan lbe changed within the capacity of the machine by adjusting theeccentricity of the pins 82 and 84. Ordinarily the two pins are adjustedto have the same eccentricity but this is not always necessary.

As the wire is gripped between the feed rolls and is fed forward, thatis, toward the left as viewed in Fig. 1, it passes over or lunder anarbor 114, and against a coil ing point 116, which deiiects the wiredownward or upward, according to the adjustment of the coiling tools,and around the arbor to produce either a right or a lefthand spring. Thearbor 114 is carried by a tool holder 118, and a pitch tool 120 is alsomounted on the holder 11S. The function of the pitch tool 120 is todcect the coil after it has been formed, and to give to it the necessarypitch or space between adjacent convolutions, to which end the pitchtool is adjustable within the holder 118. The diameter of the coilformed by the coiling point 116 is determined by the relative positionsof said coiling pointand the arbor 114, and means is provided foradjusting the coiling point d uring the coiling opera.- tion. After acoil has been formed, the pitch tool 12,0 presses against the end of thecoil in such a manner as to deflect the wire continuously into a seriesof spirals of the required pitch, and the adjustment of this tool 120,as well as itsmovement during coiling, is also provided for.

Following the feeding of a predetermined length of wire and followingthe completion of a series of coils to constitute a spring, cut-olfmechanism including cutting tools 122 comes into operation to effect thesevering of the wire of the arbor 114. The cutting tools 122 are mountedon oscillatory heads 124 above and below the arbor 114, and whenright-hand springs are being coiled, the lower tool 12-2 is mounted inits head 124 so as to cooperate with the arbor 114 in cutting the wire.The upper tool 122 is then held to an inactive position, and is onlybrought into operation when forming left-hand coils.

As has been described, there may be two separate feeding movements ofthe wire during each cycle, and therefore two springs may be coiledduring each cycle. When two separate springs are formed during eachcycle, the cut-off mechanism is operated twice during each cycle. Themeans for operating the cut-off mechanism includes a horizontal camshaft 126 which is mounted in bearings in the frame members 10, 12 and14. Mounted on the shaft 126 is a gear 128 which meshes with the gear9,6. The pitch diameter of the gear 128 is one-half that of the gear 96and therefore the gear 128 and the cam shaft 126 make two rotationsduring each rotation of the gear 96, that is, two rotations during eachcycle of the machine. The cam shaft 126 operates the cut-olf mechanismand may also operate a mechanism for controlling the diameters of thesprings during coiling and a mechanism for controlling the pitches ofthe springs during coiling. The three last said mechanisms are or may bethe same as disclosed in the said Patent 2,119,002 and they need be onlybriey described.

As best shown in Fig. 2, the heads 124 carrying the cutters 122 aremounted on shafts 130, 130 rotatably supported in parallel relationbetween the frame members.

10 and 12. The upper shaft 130 carries a collar 132, from which projectsan arm 134 pivotally connected to a link 136 which extends downwardlyand is indirectly connected at its lower end with an arm 138 mounted ona pivot shaft 140. The arm 138 carries a roll 142 bearing on a cam 144mounted on the cam shaft 126, the cam 144 being so designed that anoscillatory movement is imparted to the upper cutter Shaft during eachcomplete rotation of the cam shaft 126. The mechanism for moving thelink 136 is similar to the mechanisms hereinafter described in greaterdetail for moving similar links for diameter control and for pitchcontrol. Turning movement of the upper cutter shaft 130 is imparted tothe lower shaft 1,30 by means of arms 146 mounted on the shafts andconnected by link 148, s o that the cutter heads 124 are adapted forsynchronous turning movement, although in opposite directions withrespect to the coiling arbor 114. The cam 144 imparts two movements tothe link 136 during each cycle, the appropriate cutter 122 beingactuated twice during each cycle and serving in each instance to severthe Wire and to separate a completed spring. The positions of the cam144 on the shaft 126 is such that the cutter 122 engages and severs thewire during each of the intervals D and E between successive feedingperiods A and C as indicated in Fig. 7. p

The coiling point 116 consists of a bar having a groove at its end toreceive the wire being coiled, and is carried lby a holder 150 mountedon a pin 152 forming part of a slide 154 movable at right angles to theaxis of coiling. Reciprocatory movement is imparted to the slide 154 bymeans of a link 156 connected at its ends to a pink on the slide and toaV crank arm 158. The arm 158 is turnable with a shaft v160 extendingthrough the ,iframe member lo'land'provided at its inner end with anoperating arm 162. The arm 162 is connected by `a. link 164 to a lever166 pivoted on a horizontal pivot rod 168. The lever 166 cooperates withan arm 170 pivoted on said horizontal pivot shaft 140. The arm 170carries `a rol1`174 bearing on the face of a cam 176 mounted on theshaft 126. In order to provide for adjustment of the form of a spring,the lever 166 carries an adjustable block 178, whereby the point ofapplication of the force exerted by the cam roll arm 170 may be variedwith respect to the pivot of the lever 166. The several elements of themechanism for actuating the slide 154 are maintained in operativerelation by means of a spring 180. r With the parts arranged as shown,each complete rotation of the cam'176 causes the coiling point slide 154to inoveback and forth, with reference to the coiling axis,-'and-thereby causes the coiling point 116 to control the diameter ofthe spring being coiled. By varying the yforint of the cam 176, it ispossible to produce springs of varying contour, such as cone springs,barrel springs or two-diameter springs. The cam 176 imparts twomoveinents to the Adiameter control mechanism during each cycle, and ittherefore serves to control the diameters of two springs during eachcycle. The cam 176 acts during the feeding intervals A and C asindicated in Fig. 7. The pitch tool 120 has a shank not shown extendingrearwardly through an opening in the tool holder 118 and fpivotallyconnected to a link 184 which is shown in Fig. 2. The other end of thelink 184 is connected to one arm of a bell crank lever 186, pivotallymounted at 188. The other arm of the lever 186 is connected by anadjustable link 189 to a lever 190 similar to the lever 166 and .mountedon the same pivot rod 168. A cam 192 on the cam shaft 126 serves tooperate the link 188 by mechanism similar to that shown and describedfor the link :164. The pitch tool may be m-oved by the mechanismreferred to during the coiling of a spring so as to vary the pitch ofthe spring as required.

With the parts arranged as shown, the pitch may be varied as the springis coiled. The cam 192 imparts two movements to the pitch controlmechanism during each cycle, and it therefore serves to control thepitches of two springs during each cycle. The cam 192 acts during thefeeding intervals A and C as indicated in Fig. 7

After a spring has been coiled with the desired diameter and pitch, asdetermined by the functioning of the coiling point 116 and of the pitchtool 120, the feed rolls come to rest, or are inactive, and one of the[cutter] .cutters 122 operates to sever the completed coil in one of theintervals [C and D] D and E between successive feeding movements of thewire. The mechanisms for diameter control and for pitch control and forcut-off yoperate twice during each cycle.

The machine as shown in Figs. l to 3 may be variously adjusted fordifferent manners of use, and one adjusty ment and manner of usehavebeen described in detail .for the making of two springs per cycle.In some instances it may be desirable to make yone relatively longspring per cycle instead of two short ones. The invention makes itpossible to make much longer springs than would be possible with aconventional machine such as that shown in Patent 2,119,002. In orderthat the machine may make `one long spring per cycle, gearing isYprovided for causing the cam shaft 126 to make one rotation per cycleinstead of two rotations per cycle.

As shown, the gear 128 which provides two cam shaft notations per cycleis longitudinally movable on the shaft 1,26 to an inoperative positiontoward the left from the position'shown in Fig. 3. The gear may have anannularly grooved hub and a gear shift yoke, not shown, may be enteredin the groove in the hub for moving the 4gear 4from and to its operativeposition. Rigidly conlnected with the gear 94 for rotation therewith isa gear ses@ 194. A gear-196 is longitudinally movableon the lshaft 126and is adaptedto'mesh with the gear 194 Vwhen moved to an operativeposition toward the left from Vthe position shown in Fig. 3. The twogears 194 and 196 have the same pitch diameters. The gear 196 may havean annularly grooved hub and a gear shift yoke, not shown, may beentered in the groove in the hub for moving the gear to and from itsoperative positions, With the gears 128 and 196 both shifted toward theleft, the cam shaft 126 will have one rotation per cycle instead of tworotations per cycle.

The feeding of the wire is not in any way aiected by the cam shaftrotation, and there are two feeding periods A and C with intervals D andE between them, as indicated in Fig. 7.v However, the cut-off mechanismoperates only once per cycle in one or the other of intervals D and E.Assuming that cut-off takes place during the interval D, it will -beseen that feeding takes place during the periods C and A, the amount offeeding being twice what it was for the first described adjustment ofthev machine, wherein the cut-off mechanism operates twice during eachcycle. The cams 176 and 192 for controlling diameter and for controllingpitch operate exactly as previously described, but the cams must be sodesigned as to take into account the two separate feeding movements ofthe wire with an interval between the said feeding movements.

-nsm and the pitch control mechanism and the cut-oif mechanism will notoperate. The coiling point 116 and the pitch tool 120 are manually setin fixed positions to provide the spring with the required diameter andpitch.

The direction of rotation of the drive shaft 62 is rcversed by reversingthe drive motor or otherwise. With reversed rotation of the drive shaft,the gears 94 and 96 and the crankpins 82 and 84 will rotate in thecounterclockwise direction instead of in the clockwise direction. Itwill be apparent from Fig. 4 that, with the direction of rotationreversed, the pin 82 moves countercl'ockwise from the extreme rightposition 82a to the opposite extreme left position 82h andcorrespondingly movesthe segment 68 and the gear 74 in a period that isa little more than a half-cycle as represented by B, and the action ofthe clutch 78 is such that the feed rolls rotate in the feedingdirection during said period. The pin 8,2 then moves counterclockwisefrom the left position 82b to the right position 82a and correspondinglymoves the segment 68 and the gear 74 in a period that is a little lessthan a half-cycle. There is no feeding by the clutch 78 during the lastsaid period. It will be observed that during the feeding movement of thepin 82 from position 82a to position 82b the gear 74 is rotatedrelatively slowly and during the return movement of the pin from theposition 82b to the position 82a said gear is rotated relativelyrapidly. As Will be apparent from Fig. 5, the pin 84 movescounterclockwise from the extreme right position S4a to the extreme leftposition 84b and correspondingly moves the segment 70 and the gear 76 ina period B that is a little more than a half-cycle, and the action ofthe clutch is such that the feed rolls rotate in the feeding directionthrough the last said period. The pin 84 then moves counterclockwisefrom the left position 84b to the right position 84 and correspondinglymoves the segment 70 and the gear 76 in a period that is a little lessthan a half-cycle. There is no feeding by the clutch 80 during the lastsaid period. It will be observed that during the feeding movement of thepin 84 .springs of indefinite length.

Voverlap lfor continuous feeding,

essais relatively slowly "and during :the return f-movernent of "the pinr:from the position 84b to the-position '84B4 said gear is rotatedrelatively rapidly. The two periods of rotation of the feed rollsresulting from the action of the segments 68 and '70 are within the samecycle but they are in opposite phase. inasmuch as'each of the periods ismore than a half-cycle, said periods overlap yto provide uninterruptedfeeding so as to make it possible to coil The v overlapping feedingperiods are shown in Fig. 8 which isf-similar to Fig. 7 in 'that the twofeeding periods are shown in their proper phase relationship. Fig. 8shows that the feeding periods 'whereas as shown in Fig. 7the'feedinglperiods'arevspaced `to provide intervals for cut-off.

The machine embodying 'the linvention can be adjusted to operate -in thesame manner as Va standard machine as shown in the said patent. To thisend the gear 128 is moved to its inoperative position and the gear 196is moved to its operative position so that the cam shaft 126 makes onerevolution for each cycle. One or the other of the gear segments 68 and70'is made inoperative by adjusting the corresponding pin 82 or 84 toits dead center position. The direction of rotation of ythe drive shaftis reversed by reversing the drive motor or otherwise.

Figs. 9 and l0 show schematically an alternative embodiment of theinvention. In Athis alternative embodiment the recip-rocable means is asingle reciprocable member instead of two such members, said memberbeing shown as a single oscillable gear segment 198 instead of twoseparate gear segments such as 68 and 70. The gear segment 198 lmay bepivoted on the beforementioned pivot rod 72. For oscillating the gearsegment 198 there is provided a suitable means which is preferablyconstructed and arranged to cause said member to move at the same rateinboth directions. Said oscillating means is shown as including acrankpin 200 which may be similar to the crankpins 82 and 84 and whichis carried by a'gear 202 similar to the -gears 94v and 96. The gear 202is driven by ya gear 204 on a main drive shaft 206, this drive l,shaftbeing similar to the drive shaft 62 but dilferently-positioned. Thecrankpin 200,-instead of directly engaging the gear segment 198, isconnected therewith by a link 208 Which-is ypivoted to the segment at210 and which has an opening 212 near the other end, the 'pin 200 beingentered in 'the opening.

A .gear 214 'is mounted on the vfeed shaft -60, being connectedltherewith by a unidirectional clutch v216, the clutch serving to drivethe feed sha-ft only `when the gear 214 is rotated in the clockwisedirection. An auxiliary feed shaft 218 is provided and a gear 220 onthis shaft meshes -with the gear 58. Also mounted `on the yauxiliaryfeed shaft 21-8 and meshing with `thegear segment is a gear 222 which issimilar to the gear 214. The gear 222 is connected with the auxiliaryfeed shaft 218 by a unidirectional clutch 224, the clutch serving todrive the auxiliary feed shaft only when the gear '222 -is rotated inthe counterclockwise direction.

Provision is made in the power connection between the gear 202 and thefeed shaft for providing a predetermined amount of lost motionIfollowing each motion of the gear segment :in at 'least one directionand preferably following each ymotion in each direction. This lostmotion provides an interval of time between successive feedingoperations during which cut-offis ef'ected This lost motion can bevariously provided, but as shown it is provided by making the opening212 `in the link a longitudinal slot.

Except as to the parts last above-described, the alternative machinedisclosed in Figs. -9 and 10 may be the same as the machine disclosed inFigs. 1 to 3 and repetition of the description is unnecessary.'Provision may be made -for causing `the cam shaft to 'havel one or tworotations for each cycle.

fFig. 19 `shows the gear segment 198 `at the completion of its movementtoward the left. In 'so moving, the lseg.- ment hasrotated the gear 214in the clockwise direction and has thus rotated the feed'shaft 60 in theclockwise direction which is the direction for feeding. The gear 222 hasalsobeen rotated in the clockwise directionybut the clutch 224 has beeninoperative and the gear 220 has been rotated idly in thecounterclockwise direction Vby yreason of its engagement with the gear58.

Fig. l0 shows the gear segment 198 at the completion of its movementtoward the right. In so moving, the segment has rotated the gear 220 inthe counterclockwisc direction and has thus rotated the auxiliary feedshaft 218 in the counterclockwise direction. The gear 220 on the shaft218 has rotated the gear 58 in the Vclockwise direction which is thedirection for feeding. The gear 214 has also been rotated in thecounterclockwis'e direction, but the clutch 216'has been 'inoperativeand hasnot interferred with the clockwise direction of the gear '58.

The slot 212 in the link 208 provides the required 'lost motion whichresults in a short dwell or interval between each movement of thesegment 198 in one direction vand its immediately following movement inthe opposite direction. Cut-olf is effected during this interval. TheAtiming of the feeding and of other operations is therefore 'the same orsubstantially the same as shown in Fig. 7.

Fig. 1'1 shows schematically another alternative embodiment of theinvention. In this alternative embodiment the reciprocable means is asingle rectilinearly movable member or rack 226 instead of apivotallymovable gear segment such as 198. The rack 226 `is rectilinearly guidedby amember 228. For reciprocating the rack 226 there is provided acrankpin 230 which may be similar to the crankpins 82 and 84 and whichis carried by a gear 232 similar to the gears 94 and 96. The gear 232 isdriven by a gear 234on a main drive shaft 236, this drive shaft beingsimilar to the drive shaft 62 but differently positioned. VrThe crankpin230, instead of directly engaging the rack 226, is connected therewithby a link l238 which is pivoted to the rack at 240 and which has a shortlongitudinal slot 242 into which the pin 230 -is entered. The gears andother parts for effecting feeding in the machine shown in Fig. l1 are ormay be substantially the same as those in the machine shown in Figs. 9and 10. It is unnecessary to repeat the description of the mechanism orof the manner of operation.

Fig. l2 shows schematically still another alternative embodiment of theinvention. In this alternative e'mbodiment the reciprocable means is asingle member or gear segment 244, the machine being in this respectsimilar to the machine shown in Figs. 9 and 10. For oscillating the gearsegment 244 there is provided a crankpin 246 which may be similar to thecrankpins 82 and 84 and which is carried by a gear 248 similar to thegears 94 and 96. The gear 248 is driven by a gear 250 on a main driveshaft 252, this drive shaft being similar to the drive shaft 62 butdifferentially positioned. The gear segment 244 has a radial slot 254and the pin 246 is entered in the slot. The slotis somewhat wider thanthe diameter of the crankpin with resultant lost motion for the purposestated in connection with Figs. 9 and l0.

The gears and other parts for eecting feeding in the machine shown inFig. l2 are or may be substantially the same as those in the machineshown in Figs. 9 and 10.

The machine as shown in Fig. 12 differs from that sho-wn in Figs. 9 and10 in that the -two feeding periods are not equal. Referring to Fig. 1.3it will be evident that the crankpin 246 will move from the position 246to the position 246b in a period F which is less than a half-cycle,feedingbeing effected during said period. It will also be evident thatthe crankpin will move from the position 246c to the position 246d inaperiod G which is more than a half-cycle, feeding being effected duringf 1 1 said period. There are short intervals H, H between the .saidfeeding periods.

The machine shown in Figs. 12 and 13 may be used for -making two shortsprings during each cycle or for making one relatively long springduring each cycle. The cam vshaft may be connected either for tworotations during l each cycle or for one rotation during each cycle andthe cut-off mechanism may operate either twice or once during each cyclein both or one of the intervals H, H. Inasmuch as the two feedingperiods are unequal in time, it is not readily convenient to provide forchanges in diameter or in pitch during coiling. However, the coilingpoint 116 and the pitch tool 120 may be manually set in fixed positionsto provide the springs with the required diametcr and pitch..

. Theinvention claimed is:

.1. In -a cyclically operable spring coiling machine, a reciprocablemeans having gear teeth spaced in the direction of reciprocatiommeansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with theVteeth of the reciprocable means and each rotatable theren by in onedirection during the first portion of each cycle and rotatable therebyin an opposite direction during the .second portion of each cycle, afeed shaft, feed rolls operably connected with the feed shaft andengageable with a .length of wire to effect wire feeding during rotationof the feed shaft, first and second unidirectional clutchesoperablyconnected respectively with the first and second gearswhichfirst clutch serves upon rotation of the first gear during the firstportion of the cycle to rotate the feed shaft in the direction forfeeding and which second clutch serves upon rotation of the second gearduring the second portion of the cycle to rotate the feed shaft in said,direction for feeding so that the two clutches act alternatelyl andrepetitively to effect wire feeding during the .first and secondportions of all cycles, and means engage- 'able by the wire duringfeeding movement thereof to effect wire coiling so as to thereby form aspring.

2. In a cyclically operable spring coiling machine, a Vreciprocablemeans having gear teeth spaced in the direction of reciprocation, meansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable thereby in one directionduring the first portion of each cycle and then rotatable thereby in anopposite direction during lthe second portion of each cycle, a feedshaft, feed rolls operably connected with the feed shaft and engageablewith a length of wire to effect wire feeding during rotation of the feedshaft, first and second unidirectional clutches operably connectedrespectively with the first and second gears which first clutch servesupon rotation of lthe first gear during the first portion of the cycleto rotate the feed shaft in the direction for feeding and which secondclutch serves upon rotation of the second gear during the second portionof the cycle to rotate the feed shaft in said direction for feeding sothat the two clutches act alternately and repetitively to effect asuccession of wire feeding movements during the first and secondportions of all cycles, means for providing a short interval of timewithin each cycle and between two successive wire feeding movementsduring which interval the feed shaft 4and the feed rolls are stationary,means engageable by the wire during feeding movement to effect wirecoiling so as to thereby form a spring during each cycle, and cut- "offmechanism operable during each cycle for engaging and severing the wireWhile the feed rolls are stationary.

3. In a cyclically operable spring coiling machine, a `reciprocablemeans having gear teeth spaced in the direction of reciprocation, meansfor causing lone complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable there- Iby in one directionduring the first portion of each cycle and then rotatable thereby inan'opposite direction during the second portion of each cycle, a feedshaft, feed rolls operably connected with the feed shaft and engageablewith a length of wire to effect wire feeding during rotation of the feedshaft, first and second unidirectional clutches operably connectedrespectively with the first and second gears which first clutch servesupon rotation of the first gear during the first portion of the cycle torotate the feed shaft in the direction for feeding and which secondclutch serves upon rotation of the second gear during the second portionof the cycle to rotate the feed shaft in said direction for feeding sothat the two clutches act alternately and repetitively to -effect asuccession of wire feeding movements during the first and secondportions of all cycles, means for providing short intervals of timebetween said successive wire feeding movements during -which intervalsthe feed shaft and -the feed rolls are stationary, means engageable bythe wire during each feeding movement to effect wire coiling so as tothereby form two springs during each cycle, and cut-off mechanismoperable twice during each cycle for engaging and severing the wirewhile the feed rolls are stationary after the forming of the respectivesprings.

4. In a cyclically operable spring coiling machine, a reciprocablemeanshaving gear teeth spaced in the direction of reciprocation, means forcausing one complete lreciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable .thereby in one directionvduring the first portion of each cycle and then rotatable thereby in anopposite. direction during the second portion of each cycle, a feedshaft, feed rolls operably connected with the feed shaft and engageablewith a length of wire to effect wire feeding during rotation of the feedshaft, first and second unidirectional ,clutches operably connectedrespectively with the first and second gears which first clutch servesupon rotation of thefirst gear during the first portion of the cycle torotate the feed shaft in the direction for feeding and which secondclutch serves upon rotation of the second gear during the second portionof the cycle to rotate the feed shaft in said direction for feeding sothat the two clutches act alternately and repetitively to effect asuccession of wire feeding movements during the first and secondportions of all cycles, means for providing two short intervals of timewithin each cycle and between successive wire feeding movements duringwhich intervals the feed shaft and the feed rolls are stationary, meansengageable by the wire during feeding movement to effect wire coiling soas to thereby form either one or two springs during each cycle, cut-offmechanism operable during each cycle for engaging and cutting the wirewhile the feed rolls are stationary, and means adjustable to cause thecut-off mechanism to operate once during each cycle or twice during eachcycle.

5. In a cyclically operablespring coiling machine, a reciprocable meanshaving gear teeth spaced in the direction of reciprocation,vmeans forcausing one complete reciprocation of the reciprocable means during eachcycle of the machine, first and second gears meshing with the teeth ofthe'reciprocable means and each rotatable thereby in one directionduring the first half of each cycle and .then rotatable thereby n anopposite direction and to an equal extent during the second half of eachcycle, a feed shaft, feedrolls operably connected with the feed shaftand engageable with a length of wire to effect wire feeding duringrotation -of the feed shaft, first and second vunidirectional clutchesoperably connected respectively with the first and second gears whichfirst clutch serves upon rotation of the first `gear during the firsthalf of the cycle to rotate the feed shaft in the direction for feedingand which second clutch serves upon rotation of the second gear duringthe second half of the cycle to rotate the --feed shaft in saiddirection for feeding so that the two clutches act alternately andrepetitively to effect a succession of equal wire feeding movementsduring the first and second halves of all cycles, means for providingshort intervals of time between said successive wire feeding movementsduring which intervals the feed shaft and the feed rolls are stationary,means engageable oy the wire during each feeding movement to effect wirecoiling so as to thereby form two springs during each cycle, and cut-offmechanism operable twice during each cycle for engaging and severing thewire while the feed rolls are stationary after the forming of therespective springs.

6. A spring coiling machine as set forth in claim 5, having a cam shaft,means connecting the cam shaft with the drive shaft for causing said camshaft to make two rotations during each cycle, means including a cam onthe cam shaft for operating said cut-off mechanism twice during eachcycle, and means including a cam on the cam shaft and including anelement operated by the last said cam so as to have two similarmovements during each cycle which element is engageable with the wireduring the coiling of each spring for controlling the shape of saidspring.

7. In a cyclically operable spring coiling machine, two separatelyreciprocable first and second members having teeth spaced in thedirection of reciprocation, means for causing reciprocation of saidmembers oppositely to each other during each cycle of the machine, firstand second gears meshing respectively with the teeth of said first andsecond members and rotatable respectively thereby in opposite directionsduring each cycle, a feed shaft, feed rolls operably connected with thefeed shaft and engageable with a length of wire to effect wire feedingduring rotation of the feed shaft, first and second unidirectionalclutches operably connected respectively with the first and second gearswhich first clutch serves upon each rotation of the first gear in onedirection to rotate the feed shaft in the direction for feeding andwhich second clutch serves upon `each rotation of the second gear in thelast said direction to rotate the feed shaft in said direction forfeeding so that the two clutches act alternately and repetitively toeffect wire feeding twice during each cycle, and means engageable by thewire during each feeding movement thereof to eect Wire coiling so as tothereby form a spring.

8. In a cyclically operable spring coiling machine, similar first andsecond oscillable gear segments, means for causing one completeoscillation of each gear segment during each cycle of the machine witheach segment moving in directions opposite to those of the other, firstand second gears meshing respectively with the first and second gearsegments which first gear is rotated by its segment in a feedingdirection during the first portion of each cycle and is oppositelyrotated thereby during the second portion thereof and which second gearis rotated by its segment in the said feeding direction during thesecond ,portion of each cycle and is oppositely rotated thereby duringthe first portion thereof, a feed shaft, feed rolls operably connectedwith the feed shaft and engageable with a length of wire to-effect wirefeeding during rotation of the feed shaft, first and secondunidirectional clutches operably connected respectively with the firstand second gears and serving during rotation of the first and secondgears in the said feeding ydirections thereof to rotate the feed shaftin the direction for feeding so that the two clutches act alternatelyand repetitively to effect a succession of wire feeding movements duringthe first and second portions of all cycles, means for providing shortintervals of time between said successive wire feeding movements .duringwhich intervals the feed shaft and the feed rolls are stationary, meansengageable by the wire during each feeding movement to effect wirecoiling so as to thereby form two springs during each cycle, and cut-offmechanism operable twice during each cycle for engaging and severing,the wire while the feed rolls are stationary after the forming of therespective springs.

9. In a cyclically operable spring coiling machine,

similar first and second oscillable gear segments, means for causing onecomplete oscillation of each gear segment during each cycle of themachine with each segment moving in directions opposite to those of theother, first and second gears meshing respectively with lthe first andsecond gear segments which first gear is rotated by its segmen-t in afeeding direction during the first portion of each cycle .and isoppositely rotated thereby during the second portion thereof and whichsecond gear is rotated by its segment in the said feeding directionduring the second portion of each cycle and is oppositely rotatedthereby during the first portion thereof, a feed shaft, feed rollsoperably connected with the feed shaft and engageable with a length ofwire to effect wire feeding during rotation of the feed shaft, first andsecond unidirectional clutches operably connected respectively with thefirst and second gears and serving during rotation of the first andsecond gears in the said feeding directions thereof to rotate the feedshaft in the direction for feeding so that the two clutches actalternately and repetitively to effect a succession of wire feedingmovements during the first and second portions of all cycles, means forproviding two short intervals of time within each cycle and betweensuccessive wire feeding movements during which intervals the feed shaftand the feed rolls are stationary, means engageable by the wire duringfeeding movement to effect Wire coiling so as to thereby form either oneorV two springs during each cycle, cut-off mechanism operable duringeach cycle for engaging and cutting the wire while the feed rolls arestationary, and means adjustable to cause the cut-off mechanism Vtooperate once during each cycle or twice during each cycle.

l0. In a cyclically operable spring coiling machine, two separatelyreciprocable first and second members having teeth spaced in' thedirection of reciprocation, means for causing reciprocation of saidmembers oppositely to each other during each cycle of the machine whichmeans is constructed to move each member relatively rapidly in onedirection during a relatively short period of less than half a cycle andrelatively slowly in the opposite direction during a relatively longperiod which is the remainder of the cycle, first and second gearsmeshing respectively with the teeth of said first and `second membersand rotatable respectively thereby to opposite directions and atdifferent speeds during each cycle, a feed shaft, feed rolls operablyconnected with the feed shaft and 'engageable with a length rof wire toeffect wire feeding during rotation of the feed shaft, first and secondunidirectional clutches operably connected respectively with the firstand second gears which first clutch serves upon each relatively rapidAand relatively short rotation of the first gear in one direction torotate the feed shaft Vin the direction for feeding and which second.clutch'serves upon each relatively rapid and relatively short rotationof the second gearV in the last `said direction to rotate the feed shaftin said direction for feeding so that the two ,clutches Aact alternatelyand repetitively to effect wire feeding twice during each cycle withshort intervals of time between successive feeding movements, meansengageable by the wire during each feeding movement thereof to effectwire coiling so as to thereby ,form a spring, and .cut-off mechanismoperable during each cycle for engaging and severing the wire while thefeed rolls are stationary.

ll. In a cyclically operable spring coiling machine, Similar first andsecond gear segments oscillable about a common axis kand having radialslots, two oppositely disposed crankpins rotatable about a common axisparallel with the first said axis which pins are entered respectively inthe slots in the segments, means operable for effecting one revolutionof the crankpins during each cycle of the machine so that each segmenthas one complete reciprocation during each cycle with the movement inone direction faster than that in the opposite direction, first andsecond gears 'meshingrespectively with the first and second gearsegments and each rotated by its segment alternately in a feedingdirection and to an equal extent in an opposite direction with therotation in the feeding direction faster than that in the oppositedirection, a feed shaft, feed rolls operably connected with the feedshaft and engageable with a length ofv wire to effect wire feedingduring rotation of the feed shaft, first and second unidirectionalclutches operably connected respectively with the first and second gearsand serving during rotation of the first and second gears in the saidfaster feeding direction thereof to rotate the feed shaft in its feedingdirection so that the two clutches act alternately and repetitively toeffect a succession of wire feeding movements during the first andsecond halves of all cycles, the faster rotation of the gears in saidfeeding direction providing short intervals of time between saidsuccessive wire feeding movements during which intervals the feed shaftand the feed rolls are stationary, means engageable by the 'wire duringeach feeding movement to effect Wire coiling so as to thereby form twosprings during each cycle, and cut-off mechanism operable twice duringeach cycle for engaging and severing the wire while the feed rolls arestationary after the forming of the respective springs.

12. In a cyclically operable spring coiling machine, two separatelyreciprocable first and second members having teeth spaced in thedirection of reciprocation, means for causing reciprocation of saidmembers oppositely to each other during each cycle of the machine whichmeans is constructed to move each member relatively rapidly in onedirection during a relatively short 'period of less than half of a cycleand relatively slowly in the opposite direction during a relatively longperiod which is the 4remainder of the cycle, first and second gearsmeshing respectively with the teeth of said first and second members androtatable respectively thereby in opposite directions and at differentspeeds during each cycle, a feed shaft, feed rolls operably connectedwith the feed shaft and engageable with a length of wire to effect wirefeeding during rotation of the feed shaft, first and secondunidirectional clutches operably connected respectively with the firstand second gears which first clutch serves upon each relatively slow andrelatively long rotation of the first gear in one direction to rotatethe feed shaft in the direction for feeding and which second clutchserves upon each relatively slow and Vrelatively long rotation of the'second gear in the last said direction to rotate the feed lform aspring.

13. In a cyclically operable spring coiling machine,

similar first and second gear segments oscillable about a common axisand having radial slots, two oppositely disposed crankpins rotatableabout a common axis parallel with the first said axis Whch pins areentered respectively in the slots in the segments, means operable foreffecting one revolution of the crankpins during each cycle of themachine so'that each segment has one complete reciprocation during eachcycle with the movement in one direction slower than that in theopposite direction, rst and second gears meshing respectively with thefirst'and second gear segments and each rotated by its segmentalternately in a feeding direction and to an equal extent in an oppositedirection with the rotation in the feeding direction slower than that inthe opposite direction, a feed shaft, feed rolls operably connected withthe feed shaft and engageable with a length of wire to effect wire`Vfeeding during rotation of the feed shaft, first and second-unidirectional clutches operably connected respectively with the firstand second gears and servingduring rota- ,tion of the first and secondgears in the said slower feeding direction to rotate the feed shaftinthe feeding direction so that the two clutches act alternately andrepetitively to effect a succession of wire feeding movements during thefirst and second halves of all cycles, the slower rotation of the gearsin said feeding direction causing the said feeding movements to overlapso that the wire is fed without interruption, and means engageable bythe wire during feeding movement to effect wire coiling so as to therebyform a spring.

14. In a cyclically operable spring coiling machine, a singlereciprocable member having gear teeth spaced in the direction ofreciprocation, means for causing one complete reciprocation of thereciprocable member during each cycle of the machine, first and secondgears meshing with the teeth of the reciprocable member and eachrotatable thereby in a first direction during the first portion of eachcycle and then each rotatable thereby in the reverse or second directionduring the second portion of each cycle, a feed shaft, feed rollsoperably connected with the feed shaft and engageable with a length ofwire to effect wire feeding during rotation of the feed shaft, first andsecond unidirectional clutches operably connected respectively with thefirst and second gears which first clutch is `directly connected withthe feed shaft and serves upon rotation of the first gear in the firstdirection during the first portion of the cycle to rotate the feed shaftin the direction for feeding and which second clutch is reverselyconnected with the feed shaft and serves upon rotation of the secondgear in the second direction during the second portion of the cycle torotate the feed shaft in said direction for feeding so that the twoclutches act alternately and repetitively to effect a succession of wirefeeding movements during the first and second portions of all cycles,and means engageable by the wire during feeding movement thereof toeffect wire coiling so as to thereby form a spring.

15. In a cyclically operable spring coiling machine, a singlereciprocable member having gear teeth spaced in the direction ofreciprocation, means for causing one cornplete reciprocation of thereciprocable member during each cycle of the machine, first and secondgears meshing with the teeth of the reciprocable member and eachrotatable thereby in a first direction during the first portion of eachcycle and then each rotatable thereby in the reverse or second directionduring the second portion of each cycle, a feed shaft, feed rollsoperably connected with the feed shaft and engageable with a length ofwire to effect wire feeding during rotation of the feed shaft, first andsecond unidirectional clutches operably connected respectively with thefirst and second gears which first clutch is directly connected with thefeed shaft and serves upon rotation of the first gear in the firstdirection during the first portion of the cycle to rotate the feed shaftin the direction for feeding and which second clutch is reverselyconnected with the feed shaft and serves upon rotation of the secondgear in the second direction during the second portion of the cycle torotate the feed shaft in said direction for feeding so that the twoclutches act alternately and repetitively to effect a succession of wirefeeding movements during the first and second portions of all cycles,means for providing short intervals of time between said successive wirefeeding movements during vwhich intervals the feed shaft and the feedrolls are stationary, means engageable by the wire during eachfee'dranged to cause said member to move at the same rate in bothdirections.

I7. In a cyclically operable spring coiling machine, a reciprocablemeans having gear teethspaced in the direction of reciprocation, meansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable thereby in one directionduring the first portion of each cycle and then rotatable thereby in anopposite direction during the second portion of each cycle, a feedshaft, feed rolls operably connected with the feed shaft and engageablewith a length of wire to effect wire feeding during rotation of the feedshaft, first and second unidirectional clutches operably connectedrespectively with the first and second gears which first clutch servesupon rotation of the rst gear during the first portion of the cycle torotate the feed shaft in the direction for feeding and which secondclutch serves upon rotation of the second gear during the second portionof the cycle to rotate the feed shaft in said direction for feeding sothat the two clutches act alternately and repetitively to effecta`succession of wire feeding movements during the first and Vsecondportions of all cycles, means engageable by the wire during each feedingmovement to effect wire coiling so as to thereby form at least onespring during each cycle, and cut-off mechanism automatically operableduring each cycle and after the completion of a spring for engaging andsevering the wire.

18. In a cyclically operable spring coiling machine, a reciprocablemeans having gear teeth spaced in the direction of reciprocation, meansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, frst and .second gears meshing with the teethof the reciprocable means and each rotatable thereby in one directionduring the first portion of each cycle and then rotatable thereby in anopposite direction during the second portion of each cycle, a feedshaft, feed rolls operably connected with' the feed shaft and engageablewith a length of wire to effect wire feeding during rotation of the feedshaft, first and second unidirectional clutches operably connectedrespectively with the first and second gears which first clutch servesuponl rotation of the first gear during the first portion of the cycleto rotate the feed shaft in the direction for feeding and which secondclutch serves upon rotation of the seco-nd gear during the secondportion of the cycle to rotate the feed shaft in said direction forfeeding so that the two clutches act alternately and repetitively toeffect a succession of wire feeding movements during the first andsecond portions of all cycles, means for providing a short interval oftime within each cycle and between two successive wire feeding movementsduring which interval the wire is stationary, means engageable by thewire during each feeding movement to effect wire coiling so as tothereby form at least one spring during each cycle, and cut-offmechanism automatically operable during each cycle and after thecompletion of a spring for engaging and severing the wire while saidwire is stationary.

19. In a cyclically operable spring coiling machine, a reciprocablemeans having gear teeth spaced in the direction of reciprocation, meansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable thereby in one directionduring the first portion of each cycle and then rotatable thereby in anopposite direction during the second portion of each cycle, a feedshaft, feed rolls operably connected with the feed shaft and engageablewith a length of wire to eect wire feeding during rotation of the feedshaft, first and second unidirectional clutches operably connectedrespectively with the first and second gears which first clutch servesupon rotation of the first gear during the frst portion of the cycle torotate the feed shaft in the direction for feeding and which secondclutch serves upon rotation of the second gear during the second portion.of the cycle to rotate the feed shaft in said direction for feeding sothat the two clutches act alternately and repetitively to effect asuccession of wire feeding movements during the first and secondportions of all cycles, means for providing two short intervals of timein each cycle and between said successive wire feeding movements duringwhich intervals the wire is stationary, means engageable by the wireduring each feeding movement to effect wire coiling so as to therebyform two springs during each cycle, and cut-off mechanism operable twiceduring each cycle for engaging and severing the wire while said wire isstationary after the forming of the respective springs.

20. In a cyclically operable spring coiling machine, a reciprocablemeans having gear teeth spaced in the direction of reciprocation, meansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable thereby in one directionduring the first portion of each cycle and then rotatable thereby in anopposite direction during theV second portion of each cycle, a feedshaft, feed rolls operably connected with the feed shaft and engageablewith a length of wire to effect wire feeding during rotation of the feedshaft, first and second unidirectional clutches operably connectedrespectively with the first and second gears which. first clutch servesupon rotation of the first gear during the first portion of the cycle torotateA the feed shaft in the direction for feeding and which Secondclutch serves upon rotation of the second gear during the second portionof the cycle to rotate the feed shaft in said direction for feeding sothat the two clutches act alternately and repetitively to effect asuccession of wirev feeding movements during the first and secondportions of all cycles, means for providing two short intervals of timewithin each cycie and between successive wire feeding movements duringwhich intervals the feed rolls are inactive for feeding the wire, meansengageable by the wire during each feeding movement to effect wirecoiling so as to thereby form either one or two springs during eachcycle, cut-off mechanism operable during each cycle and within at leastone of said intervals for engaging and cutting the wire, and meansadjustable to cause the cut-off mechanism to operate once during eachcycle or twice during each cycle.

21. In a cyclically operable spring coiling machine, a reciprocablemeans having gear teeth spaced in the direction of reciprocation, meansfor causing one complete reciprocation of the reciprocable means duringeach cycle of the machine, first and second gears meshing with the teethof the reciprocable means and each rotatable thereby in one directionduring the first half of each cycle and then rotatable thereby in anopposite direction and to an equal extent during the second half of eachcycle, a feed shaft, feed rolls operably connected with the feed shaftand engageable with a length of wire to effect wire feeding duringrotation of the feed shaft, first and second unidirectional clutchesoperably connected respectively with the first and second gears whichfirst clutch serves upon rotation of the first gear during the firsthalf of the cycle to rotate the feed shaft in the direction for feedingand which second clutch serves upon rotation of the second gear duringthe second half of the cycle to rotate the feed shaft in said directionfor feeding so that the two clutches act alternately and repetitively toeffect a succession of equal wire feeding movements during the rst andsecond halves of all cycles, means for providing short intervals of timebetween said successivel wire feeding movements during which intervalsthe feed rolls are inactive for feeding the wire, means engageable bythe wire during each feeding movement to effect wire coiling so as tothereby form two springs during each cycle, and cut-off mechanismoperable twice during each cycle for engaging and severing the wireduring said intervals and after the forming of the respective springs.

first and second gears meshing respectively with the first and secondgear segments which first gear is rotated by its segment in a feedingdirection during the first portion of each cycle and is oppositelyrotated thereby during the second portion thereof and which second gearis rotated by its segment in the said feeding direction dur# ing thesecond portion of each cycle and is oppositely rotated thereby duringthe first portion thereof, a feed shaft, feed rolls operably connectedwith the feed shaft and engageable with a length of wire to effect wirefeeding during rotation of the feed shaft, first and secondunidirectional clutches operably connected respectively with the firstand second gears and serving during rotation of the first and secondgears in the said feeding directions thereof to rotate the feed shaft inthe direction for feeding so that the two clutches act alternately andrep-etitively to effect a succession of wire feeding movementsA duringthe first and second portions of all cycles, means for providing shortintervals of time between saidv successive wire feeding movements duringwhich intervals the feed rolls are inactive for feeding the wire, meansengageable by the wire during each feeding movement to effect wirecoiling so as to thereby form two springs during each cycle, and cut-]?tmechanism operable twice during each cycle for engaging and severing thewire during said intervals and after the forming of the respectivevsprings.

23. In a cyclically operable spring coiling machine, similar first andsecond oscillable gear segments, means for causing one completeoscillation of each gear segment during each cycle of the machine witheach segment moving in directions opposite to those of the other, firstand second gears meshing respectively with the first and second gearsegments which first gear is rotated by its segment in a feedingdirection during the first portion of each cycle and is oppositelyrotated thereby during the second portionV thereof and which second gearis rotated by its segment in the said feeding direction during thesecond portion `of each cycle and is oppositely rotated thereby duringthe first portion thereof, a feed shaft, feed rolls operably connectedwith the feed shaft and engageable with a length of wire to effect wirefeeding during rotation of the feed shaft, first and secondunidirectional clutches operably connected respectively with the firstand second gears and serving during rotation of the first and secondgears in the said feeding directions thereof to rotate the feed shaft inthe direction for feeding so that the two clutches act alternately andrepezitively` to effect a succession of wire feeding movements duringthe first and second portions of all cycles, means for providing twoshort intervals of time within each cycle and between successive Awirefeeding movements during which intervals the feed rolls are inactive forfeeding the wire, means engageable by the wire during feeding movementto effect wire coiling so as to thereby form either one or two springsduring each cycle, cut-off mechanism operable during each cycle forengaging andcutting the wire while the feed rolls are inactive, andmeans adjustable to cause the cut-off mechanism to operate once duringeach cycle or twice'during each cycle.

References` Cited in the le of this patent or the original patent UNITEDSTATES PATENTS 43,558 Akins July 19, 1864 236,717 Nichols Ian. 18, 1881285,372 Babcock Sept. 25, 1883 1,413,970 Curioni Apr. 25, 1922 1,516,734Johnson Nov. 25, 1924 1,555,745 Carrasco Sept. 29, 1925 2,119,002Bergevin May 31, 1938 2,170,984 Bergevin Aug. 29, 1939 2,337,420Spaulding Dec. 21, 1943 FOREIGN PATENTS 355657` France June 27, 190520,707 Astria July 25, 1905 373,727 France Mar. 27, 1907 387,477 FranceMay 7, 1908

